EP0412076A1 - Internal combustion engine with supercharger - Google Patents

Internal combustion engine with supercharger Download PDF

Info

Publication number
EP0412076A1
EP0412076A1 EP90890219A EP90890219A EP0412076A1 EP 0412076 A1 EP0412076 A1 EP 0412076A1 EP 90890219 A EP90890219 A EP 90890219A EP 90890219 A EP90890219 A EP 90890219A EP 0412076 A1 EP0412076 A1 EP 0412076A1
Authority
EP
European Patent Office
Prior art keywords
exhaust gas
internal combustion
combustion engine
water tank
water
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP90890219A
Other languages
German (de)
French (fr)
Other versions
EP0412076B1 (en
Inventor
Wolfgang Dipl.-Ing. Kriegler
Hans Dipl.-Ing. Aufinger
Franz Dipl.-Ing. Schweinzer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
AVL List GmbH
Original Assignee
AVL List GmbH
AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by AVL List GmbH, AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH filed Critical AVL List GmbH
Publication of EP0412076A1 publication Critical patent/EP0412076A1/en
Application granted granted Critical
Publication of EP0412076B1 publication Critical patent/EP0412076B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
    • F02M25/022—Adding fuel and water emulsion, water or steam
    • F02M25/025—Adding water
    • F02M25/028—Adding water into the charge intakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B47/00—Methods of operating engines involving adding non-fuel substances or anti-knock agents to combustion air, fuel, or fuel-air mixtures of engines
    • F02B47/02—Methods of operating engines involving adding non-fuel substances or anti-knock agents to combustion air, fuel, or fuel-air mixtures of engines the substances being water or steam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/36—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with means for adding fluids other than exhaust gas to the recirculation passage; with reformers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/50—Arrangements or methods for preventing or reducing deposits, corrosion or wear caused by impurities
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Abstract

Um bei einer Brennkraftmaschine (1) mit Abgasturbolader (13), ggf. einem Ladeluftkühler (17) sowie einem Abgasrückführventil (19), welches in einer vor der Abgasturbine (9) aus dem Abgasrohr (7) abzweigenden, in Strömungsrichtung nach der Abgasturbine (9) in das Ladeluftrohr (15) einmündenden Verbindungsleitung (18) angeordnet ist, die Abgasrückführung auch im Hochlastbereich anwenden zu können, wird vorgeschlagen, eine Einrichtung, welche in den die Verbindungsleitung (18) durchströmenden Abgasteilstrom im betriebswarmen Zustand und Hochlastbereich der Brennkraftmaschine (1) Wasser einspritzt (21), vorzusehen.In the case of an internal combustion engine (1) with an exhaust gas turbocharger (13), optionally a charge air cooler (17) and an exhaust gas recirculation valve (19) which, in the flow direction after the exhaust gas turbine (7) branches off the exhaust pipe (7) in front of the exhaust gas turbine (9). 9) in the charge air pipe (15) connecting line (18) is arranged to be able to use the exhaust gas recirculation even in the high load range, it is proposed that a device that flows through the connecting line (18) exhaust gas flow in the warm operating condition and high load range of the internal combustion engine (1 ) Water injected (21) to be provided.

Description

Die Erfindung bezieht sich auf eine Brennkraftmaschine mit Ab­gasturbolader, ggf. einem Ladeluftkühler sowie einem Abgas­rückführventil, welches in einer vor der Abgasturbine aus dem Abgasrohr abzweigenden, in Strömungsrichtung nach der Ab­gasturbine in das Ladeluftrohr einmündenden Verbindungsleitung angeordnet ist.The invention relates to an internal combustion engine with an exhaust gas turbocharger, optionally a charge air cooler and an exhaust gas recirculation valve, which is arranged in a connecting line branching off the exhaust gas pipe in front of the exhaust gas turbine and opening into the charge air pipe downstream of the exhaust gas turbine.

Zur Erfüllung der zu erwartenden strengen gesetzlichen Bestim­mungen bezüglich der Stickoxid-Emissionen werden die Entwick­ler und Hersteller von Nutzfahrzeug-Dieselmotoren künftig ge­zwungen sein, die Stickoxid-Emissionen der Motoren drastisch zu reduzieren.In order to meet the expected strict legal regulations regarding nitrogen oxide emissions, the developers and manufacturers of commercial vehicle diesel engines will in future be forced to drastically reduce the nitrogen oxide emissions of the engines.

Bei den für Nutzfahrzeug-Dieselmotoren gesetzlich vorgeschrie­benen Testverfahren (Europa 13-Stufen-Test; USA Heavy Duty Transient Cycle) werden ca. 70 bis 80% der Stickoxide im Hoch­lastbereich erzeugt. Bislang galt es für undurchführbar, im Hochlastbereich die bisher im unteren Lastbereich zur Reduk­tion des Stickoxids mit Erfolg praktizierte Abgasrückführung einzusetzen, da einerseits mit einem starken Anstieg der Rauch- und Partikelemission zu rechnen war, und anderseits die Dauerhaltbarkeit durch erhöhten Verschleiß beeinträchtigt würde. Der erhöhte Verschleiß tritt dadurch auf, da es bei un­gereinigten Dieselabgas zu einem Eintrag von Feststoffparti­keln über den Ölfilm der Zylinderwand in das Motoröl kommt. Ferner war zu erwarten, daß durch die Abgasrückführung in den Hochlastpunkten die Ladelufttemperatur stark erhöht würde, was einen NOx-fördernden Einfluß auf die Verbrennung hätte, wo­durch die NOx-Senkung durch die Abgasrückführung stark beein­trächtigt würde.In the test procedures required by law for commercial vehicle diesel engines (Europe 13-step test; USA Heavy Duty Transient Cycle), approx. 70 to 80% of the nitrogen oxides are generated in the high-load range. Until now, it was unworkable to use the exhaust gas recirculation that was previously successfully used in the lower load range to reduce nitrogen oxide in the high-load range, since on the one hand a strong increase in smoke and particle emissions was to be expected, and on the other hand the durability would be impaired by increased wear. The increased wear occurs because in the case of unpurified diesel exhaust, solid particles are introduced into the engine oil via the oil film in the cylinder wall. Furthermore, it was to be expected that the exhaust gas recirculation would greatly increase the charge air temperature at the high-load points, which would have an NO x -promoting influence on the combustion, which would greatly impair the NO x reduction by the exhaust gas recirculation.

Ein Großteil heutiger Nutzfahrzeug-Motoren ist, wie eingangs angegeben, zur Verbrauchs- und NOx-Senkung mit einer La­deluftkühlung versehen. Eine Abgasrückführung im Hochlastbe­reich wäre nur dann sinnvoll, wenn das rückgeführte Abgas vor dem Ladeluftkühler dem Ansaugluftstrom hinzugefügt wird. Diese Vorgangsweise verbietet sich allerdings wegen des Umstandes, daß für eine ausreichende Kühlung ein unakzeptabler Bau- und Energieaufwand erforderlich wäre. Außerdem würden die im rück­geführten Abgas konventioneller Brennkraftmaschinen enthalte­nen Partikel durch Ablagerung zur Verschmutzung und damit zur Unwirksamkeit bzw. Verstopfung des Ladeluftkühlers führen. Also bliebe nur die Möglichkeit, das rückgeführte Abgas zu reinigen oder ungereinigt unter Inkaufnahme einer Verunreini­gung und Aufheizung der Ladung nach dem Ladeluftkühler dem An­saugluftstrom beizufügen.A large part of today's commercial vehicle engines, as stated at the beginning, is provided with charge air cooling to reduce consumption and NO x . Exhaust gas recirculation in the high-load range would only make sense if the recirculated exhaust gas was present the intake air cooler is added to the intake air flow. However, this procedure is prohibited because of the fact that an unacceptable amount of construction and energy would be required for adequate cooling. In addition, the particles contained in the recirculated exhaust gas from conventional internal combustion engines would lead to contamination and thus to the ineffectiveness or clogging of the charge air cooler. So there would only be the possibility to clean the recirculated exhaust gas or to add it to the intake air flow unpolluted while accepting contamination and heating of the charge after the charge air cooler.

Es ist auch bekannt, zur Kühlung des Zylinderkopfes und des Kolbens von Hochleistungsmotoren, insbesondere Rennmotoren, Wasser in den Verbrennungsraum einzuspritzen. Als Nebeneffekt wurde dabei eine Reduzierung der Stickoxid-Emission festge­stellt.It is also known to inject water into the combustion chamber to cool the cylinder head and the piston of high-performance engines, in particular racing engines. As a side effect, a reduction in nitrogen oxide emissions was found.

Der Erfindung liegt die Aufgabe zugrunde, bei einer Brenn­kraftmaschine der eingangs genannten Art die oben angegebenen Nachteile zu vermeiden und bei Anwendung einer Abgasrückfüh­rung im Hochlastbereich zur Reduzierung der Stickoxid-Emissio­nen des Motors die Ladelufttemperaturerhöhung möglichst gering zu halten.The invention has for its object to avoid the disadvantages indicated above in an internal combustion engine of the type mentioned and to keep the charge air temperature increase as low as possible when using exhaust gas recirculation in the high-load range to reduce the nitrogen oxide emissions of the engine.

Die Erfindung besteht in einer Einrichtung, welche in den die Verbindungsleitung durchströmenden Abgasteilstrom im be­triebswarmen Zustand und Hochlastbereich der Brennkraftma­schine Wasser einspritzt. Dabei wird die eingespritzte Wasser­menge verdampft und kühlt durch die entzogene Verdampfungs­wärme den Abgasteilstrom. Die eingespritzte Wassermenge wird durch das Abgas, bzw. durch das Luft- Abgasgemisch in den Zy­linder transportiert, wobei die bekannte stickoxidsenkende Wirkung der Wassereinspritzung ausgenützt wird.The invention consists in a device which injects water into the partial exhaust gas stream flowing through the connecting line in the warm operating state and high-load range of the internal combustion engine. The amount of water injected is evaporated and cools the partial exhaust gas flow through the heat of evaporation extracted. The amount of water injected is transported into the cylinder by the exhaust gas or by the air-exhaust gas mixture, the known nitrogen oxide-lowering effect of the water injection being exploited.

Neuere Verbrennungsentwicklungen bei Nutzfahr­zeug-Dieselmotoren haben gezeigt, daß diese Motoren im hohen Lastbereich so partikelarm gemacht werden können, daß eine 10 bis 20%ige Abgasrückführrate auch ohne vorherige Reinigung und Zugabe nach dem Ladeluftkühler möglich erscheint. Durch die Partikelarmut des rückgeführten Abgases ist auch das Problem des erhöhten Motorverschleißes als Folge der Schmierölver­schmutzung durch die Abgasrückführung vermindert.Recent combustion developments in commercial vehicle diesel engines have shown that these engines can be made so low in particles in the high load range that a 10 to 20% exhaust gas recirculation rate appears possible without prior cleaning and addition after the charge air cooler. The problem is also due to the low particle content of the recirculated exhaust gas the increased engine wear as a result of the lubricating oil contamination due to the exhaust gas recirculation.

In weiterer Ausgestaltung der Erfindung ist vorgesehen, daß die Einrichtung zur Wassereinspritzung einen Wassertank sowie eine daran angeschlossene Vorpumpe aufweist, die an ein elek­tronisch gesteuertes Einspritzventil angeschlossen ist, wobei die Wasser-Einspritzmengen im Motorkennfeld in der Mo­torelektronik abgelegt sind.In a further embodiment of the invention, it is provided that the device for water injection has a water tank and a backing pump connected to it, which is connected to an electronically controlled injection valve, the water injection quantities being stored in the engine electronics in the engine map.

Es ist besonders vorteilhaft, wenn, nach einem weiteren Merk­mal der Erfindung, das Wasser-Einspritzventil in der Ver­bindungsleitung - in Strömungsrichtung des Abgasteilstromes - hinter dem Abgasrückführventil angeordnet ist.It is particularly advantageous if, according to a further feature of the invention, the water injection valve is arranged in the connecting line - in the flow direction of the partial exhaust gas flow - behind the exhaust gas recirculation valve.

Für eine gute Vermischung und Verdampfung des in den Ab­gasteilstrom eingespritzten Wassers kann erfindungsgemäß das Wasser-Einspritzventil vom Abgasteilstrom umfaßt sein.For a good mixing and evaporation of the water injected into the partial exhaust gas stream, the water injection valve can be included in the partial exhaust gas stream according to the invention.

Zur Schonung des Wasser-Einspritzventiles kann im Rahmen der Erfindung vorgesehen sein, daß dieses Wasser-Einspritzventil durch eine in den Wassertank rücklaufende Spülwassermenge ge­kühlt ist.In order to protect the water injection valve, it can be provided within the scope of the invention that this water injection valve is cooled by an amount of flushing water flowing back into the water tank.

Für den Winterbetrieb kann ferner in Ausgestaltung der Erfin­dung eine Beheizungseinrichtung für den Wassertank vorgesehen sein, wobei z.B. im Wassertank ein Temperaturfühler vorgesehen sein kann, der über die Motorelektronik bei Vereisung eine Drosselklappe in einer Nebenschlußleitung des Abgasrohres öff­net, wodurch Auspuffgase zur Erwärmung durch den Wassertank geleitet werden.For winter operation, a heating device for the water tank can also be provided in an embodiment of the invention, e.g. A temperature sensor can be provided in the water tank, which opens a throttle valve in a shunt line of the exhaust pipe via the motor electronics when icing, whereby exhaust gases are passed through the water tank for heating.

Schließlich ist erfindungsgemäß vorgesehen, daß ein im Wasser­tank angeordneter Temperaturfühler über die Motorelektronik eine elektrisch betriebene Beheizungseinrichtung für den Was­sertank steuert.Finally, it is provided according to the invention that a temperature sensor arranged in the water tank controls an electrically operated heating device for the water tank via the motor electronics.

Die Erfindung wird anhand des in der Zeichnung schematisch dargestellten Ausführungsbeispieles näher erläutert.The invention is explained in more detail with reference to the exemplary embodiment shown schematically in the drawing.

Die Brennkraftmaschine, generell mit 1 bezeichnet, weist einen Zylinder 2, einen Zylinderkopf 3, einen hin- und hergehenden Kolben 4 sowie ein Einlaßventil 5 und ein Auslaßventil 6 auf. Das an das Auslaßventil 6 anschließende Abgasrohr 7 ist mit dem Spiral-Gehäuse 8 der Abgasturbine 9 strömungsverbunden. Das Laufrad 9′ der Abgasturbine 9 ist mit dem Laufrad 10′ des Luftverdichters 10 über die Welle 11 drehfest verbunden. Das Spiral-Gehäuse des Luftverdichters 10 ist mit 12, der aus Ab­gasturbine 9 und Luftverdichter 10 gebildete Turbolader ist generell mit 13 bezeichnet. In das Spiral-Gehäuse 12 des Luft­verdichters 10 strömt über den Stutzen 14 axial Frischluft ein; die verdichtete Ladeluft strömt aus diesem Spi­ral-Gehäuse 12 über das Ladeluftrohr 15 und den Sammler 16 zum Einlaßventil 5, wobei sie den Ladeluftkühler 17 passiert.The internal combustion engine, generally designated 1, has a cylinder 2, a cylinder head 3, a reciprocating piston 4 and an inlet valve 5 and an outlet valve 6. The exhaust pipe 7 adjoining the exhaust valve 6 is included the volute casing 8 of the exhaust gas turbine 9. The impeller 9 'of the exhaust gas turbine 9 is rotatably connected to the impeller 10' of the air compressor 10 via the shaft 11. The spiral housing of the air compressor 10 is designated by 12, the turbocharger formed from exhaust gas turbine 9 and air compressor 10 is generally designated by 13. Fresh air flows axially into the spiral housing 12 of the air compressor 10 via the connector 14; the compressed charge air flows out of this spiral housing 12 via the charge air pipe 15 and the collector 16 to the inlet valve 5, passing through the charge air cooler 17.

Zwischen dem Abgasrohr 7 und dem Ladeluftrohr 15 ist eine Ver­bindungsleitung 18 vorgesehen, über welche, gesteuert durch das hier nicht näher zu beschreibende elektropneumatisch be­triebene Abgasrückführventil 19, ein Abgasteilstrom vom Abgas­rohr 7 zum Ladeluftrohr 15 in Richtung des Pfeiles 20 über­strömen kann. Der elektropneumatische Druckwandler ist mit 19′ und die Vakuumpumpe mit 19˝ bezeichnet. In die Verbin­dungsleitung 18 ist, in Strömungsrichtung des Abgasteil­stromes, hinter dem Abgasrückführventil 19 ein Wasser-Ein­spritzventil 21 so angeordnet, daß es zur besseren Durch­mischung des eingespritzten Wassers mit dem Abgasteilstrom vom Abgasteilstrom umfaßt wird. Ab der Mündungsstelle 18′ der Ver­bindungsleitung 18 am Ladeluftrohr 15 wird das Ladeluftrohr 15 bzw. das Saugrohr 16 bei betriebswarmem Zustand und Hoch­lastbereich der Brennkraftmaschine von einem Gemisch aus Luft, Abgas und Wasserdampf durchströmt, wie dies zeichnerisch durch Symbole veranschaulicht ist.Between the exhaust pipe 7 and the charge air pipe 15, a connecting line 18 is provided, via which a partial exhaust gas flow from the exhaust pipe 7 to the charge air pipe 15 can flow in the direction of the arrow 20, controlled by the electropneumatically operated exhaust gas recirculation valve 19, which is not described in more detail here. The electropneumatic pressure transducer is designated 19 'and the vacuum pump 19˝. In the connecting line 18, in the direction of flow of the partial exhaust gas flow, a water injection valve 21 is arranged behind the exhaust gas recirculation valve 19 such that it is encompassed by the partial exhaust gas flow for better mixing of the injected water with the partial exhaust gas flow. From the mouth 18 'of the connecting line 18 on the charge air pipe 15, the charge air pipe 15 or the intake manifold 16 is flowed through by a mixture of air, exhaust gas and water vapor in the warm operating condition and high load range of the internal combustion engine, as is illustrated graphically by symbols.

Das elektronisch gesteuerte Wasser-Einspritzventil 21 wird aus dem Wassertank 22 über die Rohrleitung 23 durch die Wasser­pumpe 24 (Vorpumpe) mit Wasser versorgt. Zwecks Kühlung des Wasser-Einspritzventiles 21 fördert die Wasserpumpe 24 eine überschüssige Spülwassermenge, welche über die Rohrleitung 25 wieder in den Wassertank zurückfließt. Ein elektrisches Steu­ergerät 26 sorgt dafür, daß die vorbestimmten Wassermengen, die dem Motorkennfeld zugeordnet sind, nur im betriebswarmen Zustand und Hochlastbereich der Brennkraftmaschine einge­spritzt werden.The electronically controlled water injection valve 21 is supplied with water from the water tank 22 via the pipeline 23 by the water pump 24 (backing pump). For the purpose of cooling the water injection valve 21, the water pump 24 conveys an excess amount of rinsing water which flows back into the water tank via the pipeline 25. An electrical control device 26 ensures that the predetermined amounts of water which are assigned to the engine map are injected only when the engine is warm and in the high-load range.

Der Abgas-Hauptstrom verläßt das Spiral-Gehäuse 8 der Ab­gasturbine 9 über den Rohrstutzen 27 und gelangt über das Aus­ puffrohr 28 zum Auspuff 29. Bei winterlichen Außentemperaturen (unter 0°C) kann über die den Wassertank 22 durchsetzende Ab­gas-Nebenschlußleitung 30 durch Öffnen der Drosselklappe 31 ein Teil des Abgashauptstromes geleitet werden. Dieser Vorgang kann automatissiert werden. Eine Vereisung des Tanks kann be­wußt zugelassen werden, da die Wassereinspritzung nach einem Kaltstart sowieso noch nicht benötigt wird. Ein Temperaturfüh­ler 32 im Wassertank 22 meldet der Steuerelektronik 26 eine eventuelle Vereisung, worauf durch das Öffnen der Drossel­klappe 31 Auspuffgase zur Erwärmung durch den Wassertank 22 geleitet werden. Ist der Tankinhalt verflüssigt, wird die Drosselklappe 31 wieder geschlossen.The main exhaust gas stream leaves the spiral housing 8 of the exhaust gas turbine 9 via the pipe socket 27 and reaches the outlet Puff pipe 28 to the exhaust 29. At wintery outside temperatures (below 0 ° C), part of the main exhaust gas flow can be passed through the exhaust gas bypass line 30 passing through the water tank 22 by opening the throttle valve 31. This process can be automated. Icing of the tank can be deliberately permitted, since the water injection after a cold start is not required anyway. A temperature sensor 32 in the water tank 22 reports any icing to the control electronics 26, whereupon exhaust gases are passed through the water tank 22 for heating by opening the throttle valve 31. If the tank content is liquefied, the throttle valve 31 is closed again.

Als Alternative zur zuvor beschriebenen Beheizung des Wasser­tanks kann auch eine elektrische Beheizung bzw. eine mit flüs­sigen oder gasförmigen Brennstoffen betriebene Heizung vorge­sehen sein. Der Wassertank ist dann allerdings bestmöglich zu isolieren.As an alternative to the heating of the water tank described above, electrical heating or heating operated with liquid or gaseous fuels can also be provided. The water tank should then be insulated as best as possible.

Das mit der Wassereinspritzung verbundene Problem der Korro­sion im Ansaugteil und Zylinder wird durch den Umstand besei­tigt, daß sich zwischen Hochlastbetrieb und Abstellen des Mo­tors immer eine Phase Teillastbetrieb ohne Wassereinspritzung befinden wird, die zur Abtrocknung eventuell benetzter Bau­teile ausreichen wird. Trotzdem ist die Verwendung sche­felarmen Kraftstoffes empfehlenswert, um Korrosionen im Aus­puff- und Abgasrückführsystem hintanzuhalten. Die erfindungs­gemäße Ausführung ist mit allen bekannten Abgasnachbehand­lungssystemen, wie Partikelfilter, Katalysator etc., kombi­nierbar.The problem of corrosion in the intake part and cylinder associated with water injection is eliminated by the fact that between high-load operation and switching off the engine there will always be a part-load operation phase without water injection, which will be sufficient to dry off any wetted components. Nevertheless, the use of low-sulfur fuel is recommended to prevent corrosion in the exhaust and exhaust gas recirculation system. The embodiment according to the invention can be combined with all known exhaust gas aftertreatment systems, such as particle filters, catalytic converters, etc.

Claims (8)

1. Brennkraftmaschine mit Abgasturbolader, ggf. einem Lade­luftkühler sowie einem Abgasrückführventil, welches in ei­ner vor der Abgasturbine aus dem Abgasrohr abzweigenden, in Strömungsrichtung nach der Abgasturbine in das Lade­luftrohr einmündenden Verbindungsleitung angeordnet ist, gekennzeichnet durch eine Einrichtung, welche in den die Verbindungsleitung (18) durchströmenden Abgasteilstrom im betriebswarmen Zustand und Hochlastbereich der Brennkraft­maschine (1) Wasser einspritzt.1.Internal combustion engine with an exhaust gas turbocharger, possibly a charge air cooler and an exhaust gas recirculation valve, which is arranged in a connecting line branching off the exhaust gas pipe in front of the exhaust gas turbine and opening into the charge air pipe downstream of the exhaust gas turbine, characterized by a device into which the connecting line (18 ) injecting partial exhaust gas flow in the warmed-up condition and high-load area of the internal combustion engine (1) water. 2. Brennkraftmaschine nach Anspruch 1, dadurch gekennzeich­net, daß die Einrichtung zur Wassereinspritzung einen Was­sertank (22) sowie eine daran angeschlossene Vorpumpe (24) aufweist, die an ein elektronisch gesteuertes Einspritzventil (21) angeschlossen ist, wobei die Was­ser-Einspritzmengen im Motorkennfeld in der Motorelektro­nik (26) abgelegt sind.2. Internal combustion engine according to claim 1, characterized in that the device for water injection has a water tank (22) and an attached backing pump (24) which is connected to an electronically controlled injection valve (21), the water injection quantities in the engine map in the engine electronics (26) are stored. 3. Brennkraftmaschine nach den Ansprüchen 1 und 2, dadurch gekennzeichnet, daß das Wasser-Einspritzventil (21) in der Verbindungsleitung (18) - in Strömungsrichtung des Abgas­teilstromes - hinter dem Abgasrückführventil (19) angeord­net ist.3. Internal combustion engine according to claims 1 and 2, characterized in that the water injection valve (21) in the connecting line (18) - in the flow direction of the exhaust gas partial flow - is arranged behind the exhaust gas recirculation valve (19). 4. Brennkraftmaschine nach Anspruch 2 oder 3, dadurch ge­ennzeichnet, daß das Wasser-Einspritzventil (21) vom Ab­gasteilstrom umfaßt ist.4. Internal combustion engine according to claim 2 or 3, characterized in that the water injection valve (21) is comprised of the partial exhaust gas flow. 5. Brennkraftmaschine nach einem der Ansprüche 2 bis 4, da­durch gekennzeichnet, daß das Wasser-Einspritzventil (21) durch eine in den Wassertank (22) rücklaufende Spül­assermenge gekühlt ist.5. Internal combustion engine according to one of claims 2 to 4, characterized in that the water injection valve (21) is cooled by a flushing water quantity flowing back into the water tank (22). 6. Brennkraftmaschine nach einem der Ansprüche 2 bis 5, da­durch gekennzeichnet, daß für den Winterbetrieb eine Be­heizungseinrichtung für den Wassertank (22) vorgesehen ist.6. Internal combustion engine according to one of claims 2 to 5, characterized in that a heating device for the water tank (22) is provided for winter operation. 7. Brennkraftmaschine nach Anspruch 6, dadurch gekennzeich­net, daß im Wassertank (22) ein Temperaturfühler (32) vor­gesehen ist, der über die Motorelektronik (26) bei Verei­sung eine Drosselklappe (31) in einer Nebenschlup­leitung (30) des Abgasrohres (28) öffnet, wodurch Aus­puffgase zur Erwärmung durch den Wassertank (22) geleitet werden.7. Internal combustion engine according to claim 6, characterized in that a temperature sensor (32) is provided in the water tank (22), which opens a throttle valve (31) in a secondary slip line (30) of the exhaust pipe (28) via the motor electronics (26) when icing , whereby exhaust gases are passed through the water tank (22) for heating. 8. Brennkraftmaschine nach Anspruch 6, dadurch gekennzeich­net, daß ein im Wassertank (22) angeordneter Temperatur­fühler (32) über die Motorelektronik (26) eine elektrisch betriebene Beheizungseinrichtung für den Wassertank (22) steuert.8. Internal combustion engine according to claim 6, characterized in that a in the water tank (22) arranged temperature sensor (32) via the motor electronics (26) controls an electrically operated heating device for the water tank (22).
EP90890219A 1989-08-03 1990-07-24 Internal combustion engine with supercharger Expired - Lifetime EP0412076B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT1875/89 1989-08-03
AT0187589A AT400473B (en) 1989-08-03 1989-08-03 INTERNAL COMBUSTION ENGINE WITH EXHAUST TURBOCHARGER

Publications (2)

Publication Number Publication Date
EP0412076A1 true EP0412076A1 (en) 1991-02-06
EP0412076B1 EP0412076B1 (en) 1993-05-26

Family

ID=3522904

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90890219A Expired - Lifetime EP0412076B1 (en) 1989-08-03 1990-07-24 Internal combustion engine with supercharger

Country Status (5)

Country Link
US (1) US5131229A (en)
EP (1) EP0412076B1 (en)
JP (1) JP2583150B2 (en)
AT (1) AT400473B (en)
DE (1) DE59001542D1 (en)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2667356A1 (en) * 1990-09-29 1992-04-03 Daimler Benz Ag DEVICE FOR CONTROLLING A BUTTERFLY OF A REGULATING VALVE OF AN EXHAUST GAS TURBOCHARGER ENGINE.
DE4319380A1 (en) * 1992-06-12 1993-12-16 Avl Verbrennungskraft Messtech IC engine with turbo charger - has nozzle diffusor unit in charging air line, with a constriction in diffusor
EP0611101A1 (en) * 1993-02-09 1994-08-17 Tennex Europe Limited Air regulating valve
AT435U1 (en) * 1991-09-02 1995-10-25 Avl Verbrennungskraft Messtech INTERNAL COMBUSTION ENGINE WITH AN EXHAUST TURBOCHARGER
DE102007001487A1 (en) * 2007-01-10 2008-07-17 Deutz Power Systems Gmbh Single or multistage supercharged internal combustion engine e.g. externally ignited internal combustion engine, operating method, involves using water obtained during single or multistage compression of charged air to cool compressor wheel
FR2931897A1 (en) * 2008-06-03 2009-12-04 Renault Sas METHOD FOR DECREASING AN EXHAUST GAS RECIRCULATION VALVE AND INTERNAL COMBUSTION ENGINE
DE102008034215A1 (en) 2008-07-23 2010-01-28 Bayerische Motoren Werke Aktiengesellschaft Internal combustion engine has exhaust turbo charger whose turbine is connected with exhaust gas outlet of internal combustion engine by exhaust manifold to guide exhaust gas which flows through exhaust gas cleaning device
CN101012925B (en) * 2007-01-31 2012-08-22 徐建明 Recycle burning utilization method reclaimed exhaust generated by combustion of hydrocarbon fuel and water or water vapour
WO2013053984A1 (en) * 2011-10-11 2013-04-18 Wärtsilä Finland Oy Internal combustion engine arrangement and operating method
FR3064026A1 (en) * 2017-03-20 2018-09-21 Flex Fuel-Energy Development (Ffed) IMPROVING A CLEANING SYSTEM FOR AN INTERNAL COMBUSTION ENGINE
DE102017116472A1 (en) 2017-07-21 2019-01-24 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Water injection device for an internal combustion engine

Families Citing this family (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9006371D0 (en) * 1990-03-21 1990-05-16 Secr Defence Active control of noise
DK170218B1 (en) * 1993-06-04 1995-06-26 Man B & W Diesel Gmbh Large pressurized diesel engine
SE502452C2 (en) * 1994-02-25 1995-10-23 Rosen Ways to supply steam to the intake air to an internal combustion engine and a device therefor
US5488932A (en) * 1994-08-01 1996-02-06 Serafini; Joseph Gaseous fuel enriching subsystem
AU3540195A (en) * 1994-08-29 1996-03-27 Anju Nelson Combustion and steam engine system and methods
SE511035C2 (en) * 1996-04-25 1999-07-26 Volvo Ab Supercharged internal combustion engine
US5694908A (en) * 1996-05-08 1997-12-09 Hsu; Chih-Cheng Auxiliary water-supply sytem for an internal combustion engine
GB2313155B (en) * 1996-05-08 1998-06-24 Hsu Chih Cheng An auxiliary water supply system for an internal combustion engine
DE19618868C2 (en) * 1996-05-10 1998-07-02 Daimler Benz Ag Internal combustion engine with an exhaust gas recirculation system
US8215292B2 (en) 1996-07-17 2012-07-10 Bryant Clyde C Internal combustion engine and working cycle
US6082311A (en) * 1996-09-09 2000-07-04 Lars Collin Consult Ab Drive arrangement and method of reducing the amount of nox in the exhaust gases from an internal combustion engine
SE517844C2 (en) * 1997-12-03 2002-07-23 Volvo Lastvagnar Ab Combustion engine arrangement and procedure for reducing harmful emissions
US6434943B1 (en) 2000-10-03 2002-08-20 George Washington University Pressure exchanging compressor-expander and methods of use
DE10055946A1 (en) * 2000-11-10 2002-05-23 Mann & Hummel Filter Internal combustion engine system has connecting line connected to exhaust feedback unit with exhaust inlet, outlet; inlet being connected to exhaust gas system, outlet to engine on inlet side
FI114112B (en) * 2001-03-14 2004-08-13 Marioff Corp Oy Method for Purifying Exhaust Gas from Internal Combustion Engine and Applying Damp Air to Internal Combustion Engine
JP3849537B2 (en) 2002-02-12 2006-11-22 株式会社デンソー Button stack failure notification device
US20050235953A1 (en) * 2002-05-14 2005-10-27 Weber James R Combustion engine including engine valve actuation system
US20050241302A1 (en) * 2002-05-14 2005-11-03 Weber James R Air and fuel supply system for combustion engine with particulate trap
CN100447385C (en) * 2002-05-21 2008-12-31 曼B与W狄赛尔公司 Large superchared explosive motor
US20040050047A1 (en) * 2002-08-21 2004-03-18 Arnold Steven Don Low speed turbo EGR
US6637382B1 (en) 2002-09-11 2003-10-28 Ford Global Technologies, Llc Turbocharger system for diesel engine
US7013879B2 (en) * 2003-11-17 2006-03-21 Honeywell International, Inc. Dual and hybrid EGR systems for use with turbocharged engine
US8555627B2 (en) * 2005-07-19 2013-10-15 Avl List Gmbh Exhaust gas line of an internal combustion engine
AT501338B1 (en) * 2006-04-26 2008-02-15 Avl List Gmbh Exhaust gas line for an internal combustion engine comprises catalyst support with regions having different physical and/or chemical properties in relation to response behavior, permeability, catalytic activity and/or thermal inertia
KR100626403B1 (en) * 2005-12-09 2006-09-20 송정헌 Water injection system for internal combustion engine
US20080115933A1 (en) * 2006-11-22 2008-05-22 Frank Robert Wilson Method and apparatus for maintaining or restoring a decreasing production from a hydrocarbon or gas well
CN102251881A (en) * 2010-05-17 2011-11-23 杨秉恒 Energy saving and emission reduction device for diesel engine
JP5772762B2 (en) * 2012-08-21 2015-09-02 株式会社デンソー Internal combustion engine
EP2923063A4 (en) * 2012-11-20 2016-08-17 Nostrum Energy Pte Ltd Internally cooled exhaust gas recirculation system for internal combustion engine and method thereof
EP2946087A4 (en) * 2013-01-17 2016-11-30 Nirmal Mulye Internally cooled internal combustion engine and method thereof
DE102013008686A1 (en) * 2013-05-22 2014-11-27 Volkswagen Aktiengesellschaft variable intake
DE102014201215B4 (en) * 2014-01-23 2022-09-29 Ford Global Technologies, Llc Partial shutdown supercharged internal combustion engine and method of operating such an internal combustion engine
CN108150318A (en) * 2017-12-06 2018-06-12 潍柴动力股份有限公司 Engine EGR gas recirculation system and its control method
KR101962468B1 (en) * 2017-12-27 2019-07-17 주식회사 현대케피코 Water injector crack prevention structure and prevention method
CN109139306A (en) * 2018-08-13 2019-01-04 北京汽车股份有限公司 Engines exhaust gas recirculation spray cooling system and method
DE102019113498B4 (en) * 2019-05-21 2021-02-25 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Apparatus and method for water injection
CN115217675B (en) * 2022-03-01 2024-03-08 广州汽车集团股份有限公司 Engine water spraying system, control method of engine water spraying system and automobile

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2977940A (en) * 1956-11-23 1961-04-04 Matthew A Theriault Method of operation of internal combustion engines
US4122679A (en) * 1973-08-10 1978-10-31 Societe D'etudes De Machines Thermiques Method and means for pre-heating the intake air of a supercharged, low-compression ratio diesel engine when operating at low load
US4270508A (en) * 1979-10-12 1981-06-02 U.S.A. 161 Developments Ltd. Combustion control system

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3970052A (en) * 1974-10-29 1976-07-20 Clemix Co. Apparatus for controlling noxious exhaust gases from internal-combustion engine
JPS5276525A (en) * 1975-12-20 1977-06-28 Ikegai Corp Exhaust gas purifier for diesel engine
JPS55109755A (en) * 1979-02-14 1980-08-23 Nissan Diesel Motor Co Ltd Exhaust gas reflux controller for diesel engine with turbo-charger
EP0055789B1 (en) * 1981-01-05 1985-04-10 Europe Economotor, Ltd. Combustion control system
JPS58206823A (en) * 1982-05-28 1983-12-02 Aisin Seiki Co Ltd Exhaust air regeneration control system of diesel engine with supercharger
US4440116A (en) * 1982-07-12 1984-04-03 Schmelzer Corporation Coolant injector
DE3236233C2 (en) * 1982-09-30 1985-07-25 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Arrangement for injecting water into a reciprocating internal combustion engine
SE442043B (en) * 1983-09-09 1985-11-25 Volvo Ab Turbocharged internal combustion engine with water injection
US4702218A (en) * 1984-07-24 1987-10-27 Mazda Motor Corporation Engine intake system having a pressure wave supercharger
JPS6197534U (en) * 1984-12-03 1986-06-23
DE3516986A1 (en) * 1985-05-10 1986-11-13 Audi AG, 8070 Ingolstadt INTERNAL COMBUSTION ENGINE WITH EXHAUST TURBOCHARGING
US4696279A (en) * 1985-08-30 1987-09-29 Combustion Control Developments, Ltd. Combustion control system
JPS62119468U (en) * 1986-01-21 1987-07-29

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2977940A (en) * 1956-11-23 1961-04-04 Matthew A Theriault Method of operation of internal combustion engines
US4122679A (en) * 1973-08-10 1978-10-31 Societe D'etudes De Machines Thermiques Method and means for pre-heating the intake air of a supercharged, low-compression ratio diesel engine when operating at low load
US4270508A (en) * 1979-10-12 1981-06-02 U.S.A. 161 Developments Ltd. Combustion control system

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 10, no. 218 (M-503)(2274) 30 Juli 1986, & JP-A-61 55358 (TOYOTA) 19 März 1986, *
PATENT ABSTRACTS OF JAPAN vol. 8, no. 54 (M-282)(1491) 10 März 1984, & JP-A-58 206823 (AISHIN SEIKI) 02 Dezember 1983, *

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2667356A1 (en) * 1990-09-29 1992-04-03 Daimler Benz Ag DEVICE FOR CONTROLLING A BUTTERFLY OF A REGULATING VALVE OF AN EXHAUST GAS TURBOCHARGER ENGINE.
AT435U1 (en) * 1991-09-02 1995-10-25 Avl Verbrennungskraft Messtech INTERNAL COMBUSTION ENGINE WITH AN EXHAUST TURBOCHARGER
DE4319380A1 (en) * 1992-06-12 1993-12-16 Avl Verbrennungskraft Messtech IC engine with turbo charger - has nozzle diffusor unit in charging air line, with a constriction in diffusor
DE4319380C2 (en) * 1992-06-12 1998-12-17 Avl Verbrennungskraft Messtech Internal combustion engine with an exhaust gas turbocharger
EP0611101A1 (en) * 1993-02-09 1994-08-17 Tennex Europe Limited Air regulating valve
DE102007001487B4 (en) * 2007-01-10 2015-07-16 Caterpillar Energy Solutions Gmbh Method and device for compressor wheel cooling of a compressor
DE102007001487A1 (en) * 2007-01-10 2008-07-17 Deutz Power Systems Gmbh Single or multistage supercharged internal combustion engine e.g. externally ignited internal combustion engine, operating method, involves using water obtained during single or multistage compression of charged air to cool compressor wheel
CN101012925B (en) * 2007-01-31 2012-08-22 徐建明 Recycle burning utilization method reclaimed exhaust generated by combustion of hydrocarbon fuel and water or water vapour
FR2931897A1 (en) * 2008-06-03 2009-12-04 Renault Sas METHOD FOR DECREASING AN EXHAUST GAS RECIRCULATION VALVE AND INTERNAL COMBUSTION ENGINE
WO2009156670A1 (en) * 2008-06-03 2009-12-30 Renault S.A.S. Method for cleaning an exhaust gas recirculation valve and internal combustion engine
DE102008034215A1 (en) 2008-07-23 2010-01-28 Bayerische Motoren Werke Aktiengesellschaft Internal combustion engine has exhaust turbo charger whose turbine is connected with exhaust gas outlet of internal combustion engine by exhaust manifold to guide exhaust gas which flows through exhaust gas cleaning device
WO2013053984A1 (en) * 2011-10-11 2013-04-18 Wärtsilä Finland Oy Internal combustion engine arrangement and operating method
FR3064026A1 (en) * 2017-03-20 2018-09-21 Flex Fuel-Energy Development (Ffed) IMPROVING A CLEANING SYSTEM FOR AN INTERNAL COMBUSTION ENGINE
WO2018172910A1 (en) * 2017-03-20 2018-09-27 Flex Fuel - Energy Development Improved cleaning installation for an internal combustion engine
US10774738B2 (en) 2017-03-20 2020-09-15 Flex Fuel—Energy Development Cleaning installation for an internal combustion engine
TWI757453B (en) * 2017-03-20 2022-03-11 法商富雷克斯燃料能源發展公司 Apparatus comprising installation for cleaning motorization system
DE102017116472A1 (en) 2017-07-21 2019-01-24 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Water injection device for an internal combustion engine

Also Published As

Publication number Publication date
AT400473B (en) 1996-01-25
US5131229A (en) 1992-07-21
DE59001542D1 (en) 1993-07-01
JPH0370850A (en) 1991-03-26
JP2583150B2 (en) 1997-02-19
EP0412076B1 (en) 1993-05-26
ATA187589A (en) 1995-05-15

Similar Documents

Publication Publication Date Title
AT400473B (en) INTERNAL COMBUSTION ENGINE WITH EXHAUST TURBOCHARGER
DE102012000543B4 (en) EXHAUST GAS RECIRCULATION SYSTEM FOR AN INTERNAL COMBUSTION ENGINE
DE102008040312B4 (en) System for controlling condensation in the intake tract of an internal combustion engine
DE102011002454B4 (en) Warming of intake air using EGR cooler in supercharged engine system with double throttle valve
DE4240239C2 (en) Internal combustion engine
EP0596855A1 (en) Internal combustion engine with exhaust gas turbocharger
DE102010027216A1 (en) Exhaust gas recirculation system for an internal combustion engine
DE112008000132T5 (en) Secondary air system for a ventilation system of an internal combustion engine
EP1653048A2 (en) Turbocompressor
DE2836870A1 (en) MOTOR VEHICLE WITH EXHAUST GAS TURBOCHARGER
DE102012219812B4 (en) Method and device for reducing the formation of condensate in front of the compressor of a turbocharged motor vehicle internal combustion engine
DE102010034131A1 (en) Method for regulating the temperature of the gas system of an internal combustion engine
DE102017106164A1 (en) turbocharger
DE4443133B4 (en) Exhaust after-treatment system of a supercharged combustion engine with particle filter and burner
WO2017140480A1 (en) Internal combustion engine and method for operating an internal combustion engine
DE3826600C2 (en) Exhaust gas turbocharger with exhaust gas cleaning device
DE102018112292A1 (en) Internal combustion engine with exhaust gas recirculation via exhaust gas compressor and pressure accumulator
DE4320045A1 (en) Supercharged internal combustion engine
DE102012219811B4 (en) A method and apparatus for reducing condensate formation upstream of the compressor of a turbocharged automotive internal combustion engine
EP4074948B1 (en) Cooling system for a reducing agent metering system and combustion engine with such a cooling system
EP0074531A1 (en) Fuel injection device
DE102021125197B3 (en) Method of operating a supercharged internal combustion engine
DE102020126135B4 (en) Combustion engine and method for internal engine reduction of nitrogen oxide emissions of a combustion engine
DE102018117124B4 (en) Internal combustion engine and method for exhaust gas aftertreatment of such an internal combustion engine
DE102019006494B4 (en) Exhaust system for an internal combustion engine of a motor vehicle, drive device for a motor vehicle and motor vehicle

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR IT NL SE

17P Request for examination filed

Effective date: 19901219

17Q First examination report despatched

Effective date: 19920414

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR IT NL SE

ET Fr: translation filed
REF Corresponds to:

Ref document number: 59001542

Country of ref document: DE

Date of ref document: 19930701

ITF It: translation for a ep patent filed

Owner name: MODIANO & ASSOCIATI S.R

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
EAL Se: european patent in force in sweden

Ref document number: 90890219.0

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20000728

Year of fee payment: 11

Ref country code: FR

Payment date: 20000728

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20000731

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010725

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020201

EUG Se: european patent has lapsed

Ref document number: 90890219.0

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020329

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 20020201

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050724

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20060116

Year of fee payment: 16

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070201